US5048803A - Hydraulically damping bearing - Google Patents

Hydraulically damping bearing Download PDF

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Publication number
US5048803A
US5048803A US07/442,159 US44215989A US5048803A US 5048803 A US5048803 A US 5048803A US 44215989 A US44215989 A US 44215989A US 5048803 A US5048803 A US 5048803A
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Prior art keywords
bearing
subchamber
spring
fluid
cavity
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Expired - Fee Related
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US07/442,159
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English (en)
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Heinrich Brenner
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ZF Friedrichshafen AG
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Boge GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/18—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper characterised by the location or the shape of the equilibration chamber, e.g. the equilibration chamber, surrounding the plastics spring or being annular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially

Definitions

  • This invention relates to a hydraulically dampening bearing which has an internal tube, an external tube located at some distance from the internal tube, and a spring, or biasing means, inserted between the internal and external tubes.
  • the bearing has sealed chambers filled with dampening fluid.
  • the chambers are connected hydraulically to one another by means of throttle passages With this configuration, the spring, or biasing means, acts simultaneously as a load spring and sealing element.
  • German Patent Publication No. P 38 10 310.9 discloses a hydraulically dampening rubber bearing for uncoupling high frequency low amplitude, oscillations by means of the chambers.
  • the bearing employs a recess which is sealed by a balancing membrane.
  • a balancing membrane is sealed by a balancing membrane.
  • the object of the invention is achieved through a bearing which has at least one chamber connected to an equalizing chamber.
  • the equalizing chamber includes an equalizing membrane, a first subchamber which contains dampening fluid and a second subchamber which may be exposed to an external pressure.
  • the connecting line which connects the chamber, or chambers, of the bearing with the equalizing chamber, is sized to accept the increased volume of the dampening fluid which is generated during temperature increases of the bearing, without increased pressure, thereby insuring the effectiveness of the balancing action performed.
  • the balancing performed by the bearing is always effective even with heat expansion of the fluid and the rubber or elastomer. This action is achieved because the pressure developed, which is above atmospheric pressure, and which would normally be produced in the hydraulic chambers, is collected by the equalizing chamber. Therefore, the walls, which balance the forces in the bearing, do not position themselves against the rigid outer walls of the bearing.
  • the length and diameter of the connecting line which may be connected to the equalizing chamber, is chosen so that during pressure thrusts within the other chambers, there are no significant dampening or currents in the connecting line. Thus only a volume equalization occurs within a short period of time.
  • the equalizing chamber is integrated with, and is a part of, a rubber, or elastomeric, bearing. In still a further embodiment of the invention, the equalizing chamber is a separate component part.
  • the equalizing membrane can be impacted with above atmospheric pressure, below atmospheric pressure or atmospheric pressure. This flexibility allows for better control of the balancing action of the bearing.
  • the equalizing membrane is impacted with below atmospheric pressure, then a small, partial amount of the dampening fluid will be drawn away from the hydraulic chambers, thereby creating a small, below atmospheric pressure and the balancing membrane of the chambers is separated a larger distance from the rigid, external tube of the bearing. This results in reduced dampening and an increase in the effectiveness of the balancing action.
  • This configuration is beneficial in conjunction with a vehicle motor since, for example, during the starting process, the motor can oscillate freely without transferring large forces to the body of the vehicle.
  • the dampening fluid is preloaded within, or transferred to, the hydraulic chambers and the distance between the balancing membrane and the external tube is reduced.
  • the dampening is, thereby, increased while a simultaneous reduction or elimination of the balancing action occurs. This could be advantageous, for example, in a vehicle travelling on extremely bad roadways when the oscillating movements of the motor of the vehicle are to be restricted.
  • the equalizing membrane is open towards the atmosphere.
  • the present invention provides a hydraulic dampening elastomeric bearing which includes an internal element, an external element for being disposed around at least a portion of the internal element and radially spaced therefrom, and a spring apparatus for being disposed between the internal element and the external element.
  • the spring apparatus defines a cavity therein.
  • an equalizing chamber for varying the hydraulic pressure in the cavity.
  • the equalizing chamber includes a first subchamber in fluid communication with the cavity apparatus, a second subchamber physically separated and fluidly sealed from the first subchamber, a sealing device for being positioned between the first subchamber and the second subchamber and for sealing the first subchamber from the second subchamber and an opening defined by the second subchamber for allowing fluid passage into and out of the second subchamber.
  • FIG. 1 is a side view, partially in section, of a hydraulic dampening bearing with an integral equalizing chamber
  • FIG. 2 is a cross-sectional view of a hydraulic dampening bearing with a separately attached equalizing chamber
  • FIG. 3 is an enlarged fragmentary sectional view of an equalizing chamber of a hydraulic dampening bearing with a connection for a control:
  • FIG. 4 is a side view, partially in section, of an internal structure of the preferred hydraulically dampening bearing, according to FIGS. 1 through 3, including various features of the invention;
  • FIG. 5 is a cross-sectional view of the hydraulic dampening bearing of FIG. 4 which has two fluid chambers;
  • FIG. 6 is an enlarged fragmentary sectional view of a valve of the bypass of the hydraulic dampening bearing shown in FIG. 5;
  • FIG. 7 is a cross-sectional view of a hydraulic dampening bearing of the invention, similar to that shown in FIG. 4, which includes a total of four chambers;
  • FIG. 8 is a cross-sectional view of a hydraulic dampening bearing of the invention of FIGS. 1 through 3, which includes three chambers;
  • FIG. 9 is a side view, partially in section, of another internal embodiment of a hydraulic dampening or elastomeric bearing of FIGS. 1 through 3, including various features of the invention in cross section;
  • FIG. 10 is a cross-sectional view of the hydraulic dampening bearing shown in FIG. 9.
  • the hydraulically dampening rubber, or elastomeric, bearing illustrated in FIG. 1 includes internal tube 1, external tube 2 which is located concentrically or eccentrically in relation to and at some distance from internal tube 1, and rubber, or elastomeric, spring 3 inserted between internal tube 1 and external tube 2.
  • Chambers 5 are provided in the form of cavities in spring 3, and are filled with dampening fluid. Chambers 5 are hydraulically connected to one another by means of a throttle passage 4.
  • Spring 3 is composed of two, preferably, identical shear elements, 3a and 3b, whereby reinforcements 9a and 9b are included for increased efficiency of assembly of the bearing.
  • Shear elements 3a and 3b have recesses 4a and 4b in facing surfaces 6. When the elements are assembled, the recesses form throttle passage 4, and bypass passage 8.
  • Connection line 7 is sealed from the atmosphere by equalizing membrane 14.
  • the inside diameter of connection line 7 is chosen to be small enough so that, during pressure surges, no significant dampening or fluid current is generated in connection line 7.
  • Chambers 5 are, additionally, equipped with recesses 10, balancing membrane 11 and venting bore 12 for the purpose of providing the balancing action of the bearing.
  • the high frequency oscillations are compensated by balancing membrane 11 without any dampening by throttle passage 4.
  • a balancing of this kind occurs only when balancing membrane 11 does not touch external tube 2 during the heating of the dampening fluid and spring 3, so that, under these circumstances, equalizing chamber 13 becomes operative.
  • FIG. 2 another embodiment of the invention is illustrated This bearing is, in principle, similar to the one shown in FIG. 1 with a difference being that equalizing chamber 13 is a separate component part.
  • Chamber 5 again is connected to subchamber 13a, of equalizing chamber 13, by means of connection line 7.
  • Equalizing membrane 14 is liquid tight and separates subchamber 13a from subchamber 13b.
  • Equalizing chamber 13, in this case, is adapted so that the atmosphere may enter through the one-sided open end of equalizing chamber 13 and can directly impact equalizing membrane 14.
  • equalizing chamber 13 is configured in such a fashion that subchamber 13b is closed off to the atmosphere by cover 15 having connection piece 16.
  • Connection piece 16 may be connected to an external pressure source so that equalizing membrane 14 can be impacted with above atmospheric pressure, below atmospheric pressure or with atmospheric pressure thereby controlling the dampening and/or balancing action of the bearing.
  • FIGS. 4-10 show greater detail of the bearings shown in FIGS. 1-3. However, for purposes of clarity, equalizing chamber 13 is not shown in FIGS. 4-10.
  • a preferred hydraulically dampening rubber, or elastomeric, bearing comprises an internal tube 1' and an external tube 2' located concentrically or eccentrically in relation to the internal tube 1' and at some distance therefrom.
  • a rubber, or elastomeric, spring or part 3' is disposed between the internal tube 1' and the external tube 2' and includes chambers 5'.
  • the chambers 5' are in the form of cavities in the rubber, or elastomeric, spring or part 3'.
  • the chambers 5' are filled with a dampening fluid and are hydraulically connected to one another by means of a throttle passage 4'.
  • the rubber spring 3' is formed and composed of two identical shear elements 3a' and 3b', each of which include reinforcements 9a' and 9b' to facilitate easy assembly.
  • the two shear elements 3a' and 3b' each include recesses 4a' and 4b' in the facing surfaces 6' thereof.
  • the recesses 4a' and 4b' respectively combine to form each of two throttle passages 4', only one of which is seen in FIG. 4'.
  • Additional recesses in the shear elements 3a' and 3b' combine, on assembly, to form a passage 8' which is designed as a bypass.
  • FIG. 5 shows a cross section of the rubber, or elastomeric, bearing shown in FIG. 4, as it would be generally seen along a plane adjacent the facing surfaces 6'.
  • the rubber, or elastomeric, spring 3' is located between the internal tube 1' and the external tube 2'.
  • the rubber, or elastomeric, spring 3' has a pair of chambers 5.1' and 5.2', which are connected to one another by means of two throttle passages 4' which are respectively located at the recesses 4a' and 4b'. Parallel to the throttle passages 4', at the recesses 4a' and 4b', there is a passage 8' in the form of a bypass.
  • a pair of valves 7', located in respective channels of the passage 8', are designed as check valves so that, at any given time, only one direction of flow through the passage 8' and one of its respective valves 7' is possible.
  • bypass flow in the passage 8' from the chamber 5.1' into the chamber 5.2' is through one of the valves 7'.
  • Bypass flow in the passage 8' from the chamber 5.2' in the reverse direction to chamber 5.1' is through the other valve 7'.
  • FIG. 6 is an enlarged fragmentary sectional view of a portion of the rubber, or elastomeric, spring 3' including one of the valves 7'.
  • Each valve 7' is respectively designed as an integral component of one of the shear elements 3a' and 3b'.
  • An adjacent portion of the other shear element 3a' and 3b' serves as a stop, or seat, for each of the valves 7' to form a combined valve element which acts as a check valve.
  • FIG. 7' shows another embodiment of a rubber, or elastomeric, bearing of the invention including the rubber, or elastomeric, spring 3' which is disposed between an internal tube 1' and an external tube 2'.
  • the chambers 5.1', 5.2', 5.3' and 5.4' are distributed around the circumference of the rubber spring 3'.
  • two of the chambers 5.1' and 5.2' are connected to one another by means of one throttle passage 4', and, on the other hand, the other two of the chambers 5.3' and 5.4' are connected to one another by means of another throttle passage 4'.
  • the throttle passages 4' are located next to one another in separate parallel planes which are displaced from one another in a direction which is perpendicular to the plane of the drawing. For each of the throttle passages 4', there is a corresponding passage 8' disposed in its corresponding plane. Each passage 8' is connected, in the form of a bypass, to be parallel to its respective throttle passage 4'. Each passage 8' includes a valve 7' which is in the form of a rubber lip. The rubber lip is capable of closing the passage 8' but can be moved to either side as a function of the pressure conditions in the chambers connected thereby.
  • each of the chambers 5.1' and 5.2' in this embodiment is respectively equipped with a recess 10', which provides decoupling by means of a membrane 11' and ventilation hole 12'.
  • the highfrequency oscillations tend to move the membrane 11' without any dampening by the throttle passage 4'. Because the configuration includes four chambers 5.1', 5.2' , 5.3' and 5.4', dampening is possible in all radial directions.
  • FIG. 8 in contrast to those shown in FIGS. 5 and 7, has three chambers 5.1', 5.2' and 5.3' which also tend to damp oscillations in all radial directions.
  • the throttle passages 4' and the bypass passages 8' are again located in a common plane at the facing surfaces 6'.
  • the chambers 5.1', 5.2' and 5.3' are all connected to one another with each of three valves 7' being capable of responding to pressure differentials in each pair of adjacent chambers 5.1', 5.2' and 5.3' in both pressure directions.
  • FIGS. 9 and 10 includes a rubber, or elastomeric, bearing of the invention in which two chambers 5' are facing the internal tube 1' as the shear elements 3a' and 3b' extend radially outward therefrom.
  • the design principle and the method of operation are the same as the examples illustrated in FIGS. 4 to 8.
  • the chambers 5' are provided with throttle passages 4' and with at least one passage 8' having a valve 7' and serving as a bypass to throttle passages 4'. With only two chambers 5', the dampening is limited to only one direction (vertically, as seen in FIG. 10).
  • the throttle passages 4' and the passage 8' are housed in the facing surfaces 6' of the two shear elements 3a' and 3b', which become functional after assembly.
  • a recess 10' is vented outwardly through a ventilation hole 12'.
  • the recess 10' is sealed from the chamber 5' by a membrane 11'.
  • the shear elements 3a' and 3b' each include an internal reinforcement 9a' and an external reinforcement 9b', so that, after assembly of the internal tube 1' and the external tube 2', the finished rubber bearing is formed.
  • All of the bearings shown in FIGS. 4-10 may employ equalizing chamber 13, if desired.
  • Patents relating to engine mount devices include U.S. Pat. No. 4,424,961, entitled “Engine Mounting For Suspending Engine Relative To Vehicle Structure” and U.S. Pat. No. 4,288,063, entitled “Rubber Elastic Engine Mounts Or Supports With Hydraulic Damping, Especially For Engine Suspensions In Motor Vehicles.”
  • Patents relating to vibration dampening devices include U.S. Pat. No. 4,781,361, entitled “Vibration-Preventing Rubber Device:” U.S. Pat. No 4,760,996, entitled “Damper and Isolator:” U.S. Pat. No. 4,753,421, entitled “Vibration-Preventing Rubber Device:” U.S. Pat. No.
  • Such rubber bearings can comprise an internal tube, an external tube located some distance from the internal tube, and a rubber piece inserted therebetween.
  • the rubber part is outwardly designed only as a seal, and is thereby subjected to tensile forces in operation. This area cannot be used as a bearing spring, and is not capable of traveling great distances in the radial direction.
  • one aspect of the invention resides broadly in a hydraulically damping rubber bearing, comprising an internal tube, an external tube located at some distance from it, and a rubber spring inserted between them, which form chambers filled with damping fluid, connected hydraulically to one another by means of throttle passages, and which are externally sealed whereby the rubber spring is being utilized as both a load spring and sealing element, is characterized by the fact that at least one chamber 5 is connected to an equalizing chamber 13 by a connecting line 7, equalizing chamber 13 is divided into subchamber 13a containing damping fluid and subchamber 13b which is impacted by external force, via equalizing membrane 14.
  • Another aspect of the invention resides broadly in a rubber bearing according to claim 1 is characterized by the fact that the equalizing chamber 13 is integrated in the rubber bearing.
  • a further aspect of the invention resides broadly in a rubber bearing according to claim 1 is characterized by the fact that equalizing membrane 14 can be impacted with above atmospheric pressure, below atmospheric pressure or atmospheric pressure.
  • a yet further aspect of the invention resides broadly in a rubber bearing according to claim 1 is characterized by the fact that subchamber 13b is open towards the atmosphere.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
US07/442,159 1988-12-07 1989-11-28 Hydraulically damping bearing Expired - Fee Related US5048803A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3841193 1988-12-07
DE3841193A DE3841193A1 (de) 1988-12-07 1988-12-07 Hydraulisch daempfendes gummilager

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US07/328,466 Continuation-In-Part US4982938A (en) 1988-03-26 1989-03-24 Hydraulic damping elastic bearing

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US5048803A true US5048803A (en) 1991-09-17

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US07/442,159 Expired - Fee Related US5048803A (en) 1988-12-07 1989-11-28 Hydraulically damping bearing

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US (1) US5048803A (enrdf_load_stackoverflow)
EP (1) EP0372169B1 (enrdf_load_stackoverflow)
JP (1) JPH02217641A (enrdf_load_stackoverflow)
DE (1) DE3841193A1 (enrdf_load_stackoverflow)

Cited By (4)

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Publication number Priority date Publication date Assignee Title
US5503376A (en) * 1993-02-25 1996-04-02 Firma Carl Freudenberg Hydraulically damping rubber sleeve spring
US5549283A (en) * 1994-10-27 1996-08-27 Hutchinson Hydraulic antivibration supports
JP2015055263A (ja) * 2013-09-10 2015-03-23 Nok株式会社 液体封入式円筒型マウント
CN111795104A (zh) * 2020-05-25 2020-10-20 中国第一汽车股份有限公司 一种液压衬套及车辆

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DE3906373A1 (de) * 1989-03-01 1990-09-13 Freudenberg Carl Fa Motorlager
US5374039A (en) * 1992-08-24 1994-12-20 Lord Corporation Fluid-and-elastomer support device
DE4301149A1 (de) * 1993-01-18 1994-07-21 Metzeler Gimetall Ag Hydraulisch dämpfendes, aktives Motorlager
DE4320643C2 (de) * 1993-06-22 1997-02-06 Hubert Dipl Ing Bruehl Hydraulisch dämpfendes Buchsenlager
DE19934637A1 (de) * 1999-07-23 2001-02-15 Contitech Vibration Control Hydraulisch bedämpfte Lagerbuchse
CN106567902B (zh) * 2015-10-13 2018-11-20 上海汽车集团股份有限公司 液压悬置及其总成、控制方法、控制单元、ecu及汽车
ITUA20164765A1 (it) * 2016-06-29 2017-12-29 F I B E T S P A Boccola idraulica

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DE2948408A1 (de) * 1979-12-01 1981-06-04 Daimler-Benz Ag, 7000 Stuttgart Elastisches lager, insbesondere fuer brennkraftmaschinen
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US4784378A (en) * 1985-11-14 1988-11-15 Ford Motor Company Vibrating body mounting assembly
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US2562195A (en) * 1945-07-07 1951-07-31 Norman E Lee Mounting
US4244240A (en) * 1976-12-17 1981-01-13 The Johns Hopkins University Elastic internal flywheel gimbal
US4215842A (en) * 1977-03-23 1980-08-05 Boge Gmbh Rubber elastic engine mounts or supports with hydraulic damping
US4288063A (en) * 1977-03-23 1981-09-08 Boge Gmbh Rubber elastic engine mounts or supports with hydraulic damping, especially for engine suspensions in motor vehicles
US4424961A (en) * 1980-05-09 1984-01-10 Nissan Motor Company, Limited Engine mounting for suspending engine relative to vehicle structure
DE3245653A1 (de) * 1982-12-09 1984-06-14 Metzeler Kautschuk GmbH, 8000 München Zweikammer-motorlager mit hydraulischer daempfung
US4708329A (en) * 1984-02-27 1987-11-24 Nissan Motor Co., Ltd. Fluid-filled power unit mount device
US4690389A (en) * 1984-08-07 1987-09-01 Avon Industrial Polymers Limited Hydraulically damped mounting device
US4721291A (en) * 1985-07-05 1988-01-26 Toyota Jidosha Kabushiki Kaisha Vibration-preventing rubber device
US4753421A (en) * 1985-07-05 1988-06-28 Toyota Jidosha Kabushiki Kaisha Vibration-preventing rubber device
US4781361A (en) * 1985-07-05 1988-11-01 Toyota Jidosha Kabushiki Kaisha Vibration-preventing rubber device
US4728086A (en) * 1986-01-20 1988-03-01 Bridgestone Corporation Vibration isolating apparatus
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US4861005A (en) * 1987-09-11 1989-08-29 General Motors Corporation Three fluid chamber mounting for resilient, vibration-damping mounting of components
US4822010A (en) * 1987-09-30 1989-04-18 Lord Corporation Fluid filled resilient bushing
DE3810310A1 (de) * 1988-03-26 1989-10-12 Boge Ag Hydraulisch daempfendes gummilager

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5503376A (en) * 1993-02-25 1996-04-02 Firma Carl Freudenberg Hydraulically damping rubber sleeve spring
US5551675A (en) * 1993-02-25 1996-09-03 Firma Carl Freudenberg Hydraulically damping rubber sleeve spring
US5549283A (en) * 1994-10-27 1996-08-27 Hutchinson Hydraulic antivibration supports
JP2015055263A (ja) * 2013-09-10 2015-03-23 Nok株式会社 液体封入式円筒型マウント
CN111795104A (zh) * 2020-05-25 2020-10-20 中国第一汽车股份有限公司 一种液压衬套及车辆

Also Published As

Publication number Publication date
EP0372169B1 (de) 1992-10-21
EP0372169A2 (de) 1990-06-13
DE3841193C2 (enrdf_load_stackoverflow) 1991-03-07
DE3841193A1 (de) 1990-06-21
EP0372169A3 (en) 1990-10-17
JPH02217641A (ja) 1990-08-30

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